CN104641080A - Actuator for axial displacement of a gas exchange valve in a combustion engine - Google Patents
Actuator for axial displacement of a gas exchange valve in a combustion engine Download PDFInfo
- Publication number
- CN104641080A CN104641080A CN201380035998.2A CN201380035998A CN104641080A CN 104641080 A CN104641080 A CN 104641080A CN 201380035998 A CN201380035998 A CN 201380035998A CN 104641080 A CN104641080 A CN 104641080A
- Authority
- CN
- China
- Prior art keywords
- actuator piston
- actuator
- valve
- fluid
- cylinder body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/16—Silencing impact; Reducing wear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
- F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
Abstract
The invention relates to an actuator for axial displacement of an object, the actuator comprises an actuator piston disc (4) and an actuator piston rod (7), which together form an actuator piston, a cylinder volume, the actuator piston disc (4) dividing said cylinder volume into a first part (5) and a second part (6) and being displaceable in said cylinder volume between an inactive and an active position, a pressure fluid circuit (10) arranged for controllable fluid communication with the first part (5) of the cylinder volume, and a first hydraulic circuit (21) comprising a liquid-filled space (22), the actuator piston rod (7) being disposed to be axially displaced in relation to said liquid- filled space (22) in connection with axial displacement of the actuator piston disc (4) in the cylinder volume. The actuator piston comprises a second hydraulic circuit (24), the liquid-filled space (22) being in fluid communication with an inner cavity (25) in the second hydraulic circuit (24) when the actuator piston disc (4) is in said inactive position, said inner cavity (25) partly being delimited by a positioning piston (29), which is displaceable in relation to the actuator piston and which is arranged to abut against said object in the second part (6) of the cylinder volume, the second hydraulic circuit (24) comprising a valve (27) that is disposed to prevent fluid flow from the inner cavity (25).
Description
Technical field
The present invention relates to a kind of actuator for moving axially object.Especially, the present invention relates to a kind of valve actuator for internal-combustion engine, wherein, suggestion uses actuator to drive one or more to enter valve or expulsion valve, and described one or more enters valve or expulsion valve controls the air supply relevant with the cylinder body of internal-combustion engine and discharge respectively.Therefore, actuator according to the present invention is particularly suited for driving engine valve, does not need one or more camshaft thus in internal-combustion engine.
Actuator according to the present invention comprises: actuator piston dish; Actuator piston bar, described actuator piston bar is fixedly connected to actuator piston dish and axially stretches out from actuator piston dish, and described actuator piston bar forms actuator piston together with actuator piston dish; Cylinder body volume, described actuator piston dish described cylinder body volume is divided into first portion and second portion and described actuator piston dish axially can move back and forth in described cylinder body volume between un-activated position and active position; Pressure fluid circuit, described pressure fluid circuit be arranged to for the first portion of cylinder body volume controllably fluid be communicated with; With the first oil hydraulic circuit, described first oil hydraulic circuit comprises fluid-filled spaces, and described actuator piston bar is arranged to along with actuator piston dish moving axially and moving axially relative to described fluid-filled spaces in cylinder body volume.
Background technique
Such as from the known actuator types mentioned by introduction of US 7,121,237 of the applicant.This section of document discloses the actuator for driving engine valve, wherein, the actuator piston bar of actuator piston has the hydraulic brake system in the region being arranged in its free end, and the mechanical stopping piece in the actuator casing of described hydraulic brake system and actuator interacts.The object of this hydraulic brake system is before the valve head contact of engine valve is arranged in the valve seat of the cylinder body of internal-combustion engine, just just reduce the movement velocity of engine valve, obtain controlled closing motion thus, to save the part that is included and reduce wearing and tearing and discord.When closed engine valve, actuator piston bar should mechanical stopping piece in contact actuator housing and the valve seat of engine valve contact engine valve, to obtain the correct braking of engine valve and actuator piston along with closed engine valve.
The most important thing is that the phase mutual edge distance between the hydraulic brake system of actuator piston bar and the valve head of engine valve is equal with the phase mutual edge distance between mechanical stopping piece and the valve seat of engine valve.Problem existing for known actuator is the mechanical stopping piece that actuator piston bar can not touch that it is arranged in actuator casing, so retarding efffect changes or do not occur retarding efffect completely.
Because engine valve is in hot environment during operation, change so size will occur the valve rod of engine valve, this directly will affect above-mentioned condition.In addition, if the production tolerance of size of the part be included is narrow, then manufacture cost will be higher, alternatively use the tolerance of size widened, then this makes to need to use the mutual alignment to regulate each part such as pad.And the part be included during operation is worn, this affects the mutual alignment of each part further.
It should be noted that except hydraulic brake system, actuator piston bar also has other function, wherein, actuator piston bar is used for different purposes relative to the position of actuator casing, for establishing the size of the first portion of cylinder body volume, be communicated with the fluid of the first portion of cylinder body volume for regulating.
Goal of the invention is sketched
The present invention is intended to eliminate the above-mentioned inferior position of previously known actuator and shortcoming and provides a kind of actuator of improvement.Main purpose of the present invention is to provide a kind of improvement actuator types limited by introduction, and described improvement actuator guarantees that actuator piston bar is always in good predetermined un-activated position when actuator is arranged in position of rest.
Inventive features is sketched
According to the present invention, at least achieve main purpose by such actuator, described actuator is limited by introduction and has the feature limited in the independent claim.In addition, the preferred embodiments of the present invention are also defined in the dependent claims.
According to the present invention, provide a kind of actuator types limited by introduction, the feature of described actuator is that actuator piston comprises the second oil hydraulic circuit, when actuator piston dish is in described un-activated position, the fluid-filled spaces of the first oil hydraulic circuit is communicated with the cavity fluid in the second oil hydraulic circuit, described inner chamber is partly defined by positioning piston, described positioning piston axially can move back and forth relative to actuator piston and be arranged to the described scavenging air valve against the second portion being arranged in cylinder body volume, described scavenging air valve is such as made up of engine valve, second oil hydraulic circuit comprises the valve being arranged to stop fluid to flow from inner chamber, actuator piston bar has free end, when actuator piston dish is in un-activated position, described free end is arranged at least in part against the stop surface in fluid-filled spaces, the pressurised zone towards inner chamber of positioning piston is equal to or less than the pressurised zone of the free end of actuator piston bar.
Therefore, the present invention is based on such understanding, by the movable positioning piston movable relative to actuator piston, can guarantee actuator piston bar engine valve be closed and actuator un-activation time be always in predetermined un-activated position.
In other preferred embodiment, actuator piston bar has hydraulic brake system in the region of its free end, and described hydraulic brake system is arranged to the movement velocity reducing actuator piston before the free end of actuator piston bar contacts described stop surface.
In other dependent claims and hereinafter other advantage of the present invention and feature as seen in detailed description of the preferred embodiment.
Accompanying drawing explanation
With reference to accompanying drawing from understand above-mentioned and further feature of the present invention and advantage more all sidedly to following the detaileds description general of preferred embodiment, wherein:
Fig. 1 is the schematic sectional side view of the actuator according to the first embodiment, and actuator piston is arranged in un-activated position;
Fig. 2 is the schematic sectional side view of the actuator shown in Fig. 1, it illustrates actuator piston and is in active position;
Fig. 3 is the zoomed-in view of a part for actuator according to Fig. 1 and Fig. 2, it illustrates the inner chamber of the second oil hydraulic circuit;
Fig. 4 is the schematic sectional side view of the actuator according to the second embodiment, and actuator piston is arranged in un-activated position; With
Fig. 5 is the schematic sectional side view of the actuator shown in Fig. 4, it illustrates actuator piston and is arranged in active position.
Embodiment
The present invention relates to the actuator that a kind of entirety by reference numeral 1 refers to, described actuator is used for moving axially object.The unrestriced object for illustration, should be used for describing the present invention with reference to one hereinafter, in the application, actuator 1, for driving one or more scavenging air valve in the cylinder body of internal-combustion engine, such as enters valve or expulsion valve.
First see figures.1.and.2, these two the first embodiments illustrated according to actuator 1 of the present invention.Actuator 1 comprises: actuator casing 2; Cylinder body 3, described cylinder body defines cylinder body volume or room; Actuator piston dish 4, described actuator piston dish can axially move back and forth in described cylinder body volume between un-activated position (Fig. 1) and active position (Fig. 2).Described cylinder body volume is divided into the first upper part 5 and the second lower part 6 by actuator piston dish 4.
In addition, actuator 1 comprises the actuator piston bar that entirety by reference numeral 7 refers to, described actuator piston bar is fixedly connected to actuator piston dish 4 and axially stretches out from described actuator piston dish, and described actuator piston bar forms actuator piston together with actuator piston dish.In the illustrated embodiment, actuator piston bar 7 has: the first thicker part divides 8, and described first thicker part divides and is arranged in actuator piston dish 4 at a distance of the position of a distance and near the hole of actuator casing 2; And second thinner section divide 9, described second thinner section is divided to divide at thicker part and to be extended between 8 and actuator piston dish 4 and to connect described thicker part and divide and actuator piston dish.
Actuator 1 also comprises the pressure fluid circuit that entirety by reference numeral 10 refers to, and described pressure fluid circuit is arranged to the first portion 5 for gas or gaseous mixture being controllably fed to cylinder body volume, for initiation pressure pulse; And be arranged to for gas or gaseous mixture are controllably given off from the first portion 5 of cylinder body volume, for the described pressure pulse of termination.
Pressure fluid circuit 10 is connected to pressure fluid source (HP) and pressure fluid remittance (LP).Pressure fluid source can be compressor, and described compressor belongs to motor and has attached groove, or can be pressure tank simply.It can be any position (such as air) of its pressure lower than the pressure produced in pressure fluid source that pressure fluid converges, or can be the pipeline turning back to compressor.
In the illustrated embodiment, actuator 1 comprises the first valve body 11 of electric control directly or indirectly, and described first valve body 11 is arranged in pressure fluid circuit 10, for the pressurised fluid flow in pilot pressure fluid circuit 10.Electric control is referred to by calutron, is controlled by piezoelectric device etc.In a preferred embodiment, actuator 1 also comprises the so-called pilot valve 12 of three-way valve form, and described pilot valve 12 is arranged to be driven by electromagnet 13.Pilot valve can also be piezo electric valve or other similar electrically operated valve.Pilot valve 12 is arranged to open alternately to activation pipe 14 be communicated with for being communicated with pressure fluid source (HP) fluid respectively and converging (LP) fluid with pressure fluid.In addition, the upper end portion of the first valve body 11 is disposed in be activated in pipe 14, and the upper end portion that the pressure fluid flowed out from pressure fluid source can act on described first valve body makes the first valve body 11 move down.Preferably by gas spring, mechanical spring etc. along first direction (towards right side) bias voltage pilot valve 12, so the activation of electromagnet 13 makes pilot valve 12 mobile along second direction (towards left side), and when electromagnet 13 is cut off, make it return by making pilot valve 12 move along another direction (towards right side).In the accompanying drawings, thus illustrate Indirect Electro and control the first valve body 11.In the example that electromagnet 13 acts directly on the first valve body 11, direct electric control first valve body 11, that is, in this embodiment, does not arrange pilot valve and activates pipe.
As shown in Figure 1, pilot valve 12 open for pressure fluid from pressure fluid source flow to activate pipe 14 time, the first valve body 11 is moved into comparatively upper/lower positions.So open the first valve body 11, flow to the first portion 5 of cylinder body volume from pressure fluid source for the pressure fluid in pressure fluid circuit, described pressure fluid source is connected with pressure fluid circuit 10.Then pressure fluid pulses will to act on actuator piston dish 4 and actuator piston dish moved to from the position shown in Fig. 1 in cylinder body volume and through the position shown in Fig. 2.Fig. 1 thus illustrate the mobile but actuator piston dish 4 of the first valve body 10 also non-setting in motion time ifm diagram.In FIG, actuator piston so to remain in its un-activated position and after this moves downward starting, to produce pressure pulse.
In fig. 2, show actuator piston dish 4 and be in its active position, and the thicker part of actuator piston bar 7 divides 8 clossing pressure fluid circuits 10, is continuously introduced to the first portion 5 of cylinder body volume to stop pressure fluid from pressure fluid source.In fig. 2, also show pilot valve 12 mobile along another direction (towards right side), converge with authorized pressure fluid and activate fluid between pipe 14 and be communicated with, pass through gas spring, mechanical spring etc. thus along upward direction bias voltage first valve body 11, described first valve body 11 is moved to comparatively goes up position, for giving off the gas in the first portion 5 of cylinder body volume, turn back to its un-activation position to allow actuator piston dish 4 from its active position.When there is discharge, actuator piston dish 4 turns back to the un-activation position shown in Fig. 1 thus.
In an illustrated embodiment, the engine valve that actuator 1 and entirety by reference numeral 15 refer to interacts, and described engine valve has valve rod 16 and valve head 17.Valve rod 16 extends through the stationary part of internal-combustion engine and enters in the cylinder body 3 of actuator 1, more accurately enter into the second portion 6 of cylinder body volume, and valve head 17 is arranged to interact with valve seat 18, for alternately allowing respectively and stoping gas/air to lead to the cylinder body of internal-combustion engine.Engine valve 15 axially can be moved by actuator 1, and the upper end portion indirectly being acted on the valve rod 16 of valve 15 by the actuator piston dish 4 of actuator 1 makes valve 15 move to its open position (Fig. 2) from its operating position (Fig. 1).And internal-combustion engine preferably includes the conventional valve spring 19 schematically shown, described valve spring 19 is arranged such that valve 15 turns back to its operating position from its open position.The underpart of valve spring 19 directly or indirectly-acting on the stationary part of internal-combustion engine, and its upper end portion acts on bracket 20 or on valve spring retainer, and described bracket or valve spring retainer are connected in the region of the upper end portion of valve rod 16.
Actuator 1 also comprises the first oil hydraulic circuit that entirety by reference numeral 21 refers to, described first oil hydraulic circuit comprises fluid-filled spaces 22, and actuator piston bar 7 is arranged to along with actuator piston dish 4 moving axially and moving axially relative to described fluid-filled spaces 22 in cylinder body volume.Liquid can flow into fluid-filled spaces 22 via safety check 23 and flow out fluid-filled spaces 22 via controlled valve, and in the illustrated embodiment, controlled valve is the first valve 11.When never active position (Fig. 1) moves to active position (Fig. 2) to actuator piston, actuator piston bar 7 is left room for making liquid flow into fluid-filled spaces 22, and when actuator piston moves to un-activation position from active position, liquid is pushed out fluid-filled spaces 22.
Now also with reference to Fig. 3, this figure shows the zoomed-in view of a part for the actuator according to the embodiment shown in Fig. 1 and Fig. 2.According to according to actuator 1 of the present invention, actuator piston comprises the second oil hydraulic circuit that entirety by reference numeral 24 refers to, and described second oil hydraulic circuit comprises inner chamber 25 then.When actuator piston dish 4 is in described un-activation position, the fluid-filled spaces 22 of the first oil hydraulic circuit 21 is communicated with inner chamber 25 fluid in the second oil hydraulic circuit 24.The first end place that internal channel 26 is being arranged in inner chamber 25 divides the second end place on the encapsulating surface of 8 to be provided with oral area with the thicker part being arranged in actuator piston bar 7.Therefore, when actuator piston dish 4 is in un-activated position, the second end of internal channel 26 should be arranged to be communicated with fluid-filled spaces 22 fluid, and preferably should cut off the connection of described fluid when actuator piston dish 4 is in active position.Second oil hydraulic circuit 24 also comprises valve 27, and described valve is arranged to stop fluid to flow to fluid-filled spaces 22 from inner chamber 25.Preferably, described valve 27 is safety check, and described safety check remains on the position of sealing internal channel 26 by check-valve spring 28.
Inner chamber 25 is partly defined by positioning piston 29, and described positioning piston axially can move back and forth relative to actuator piston, and described positioning piston is arranged to act on the engine valve 15 of the second portion 6 being arranged in cylinder body volume.Spill the second portion 6 entering into cylinder body volume through positioning piston 29 with allowing the little degree of liquid existed in inner chamber 25.
Actuator piston bar 7 has free end 30, and described free end is arranged to when actuator piston dish 4 is in un-activated position at least in part against the stop surface 31 in fluid-filled spaces 22.According in the embodiment of Fig. 1 to Fig. 3, by being arranged in spring 32 in inner chamber 25 along the direction bias voltage positioning piston 29 be biased into by positioning piston 29 in the second portion 6 of cylinder body volume.The valve head 17 of engine valve 15 touch the valve seat 18 of engine valve but the free end 30 of actuator piston bar 7 not against described stop surface 31 time, positioning piston 29 is by against engine valve 15 and spring 32 axially will up promote actuator piston until the free end 30 of actuator piston bar 7 is against stop surface 31, and liquid to be pushed in inner chamber 25 and to remain in described inner chamber simultaneously.Therefore, the function of positioning piston 29 is all positioned in tram by actuator piston when actuator piston dish 4 is in un-activated position.
Positioning piston 29 has pressurised zone, that is, the region that the region of being stretched out by the axis of positioning piston is formed, and the liquid effects in inner chamber 25, in the region that described axis is stretched out, is pulled in inner chamber 25 to stop positioning piston 29.According in the embodiment of Fig. 1 to 3, the pressurised zone towards inner chamber 25 of positioning piston 29 is equal to or less than the pressurised zone of the free end 30 of actuator piston bar 7.
In the illustrated embodiment of actuator 1 according to the present invention, actuator piston bar 7 has hydraulic brake system in the region of its free end, described hydraulic brake system is arranged to the movement velocity reducing actuator piston before the free end 30 of actuator piston bar 7 contacts described stop surface 31, thus described hydraulic brake system is arranged to the movement velocity reducing engine valve 15 before engine valve 15 contacts its valve seat 18.Hydraulic brake system is made up of the geometric contraction portion between actuator piston bar 7 and fluid-filled spaces 22, and described geometric contraction portion reduces close to described stop surface 31 along with the free end 30 of actuator piston bar 7, increases braking force thus.
Referring now to Fig. 4 and Fig. 5, these two actuators 1 illustrated according to the second embodiment.Difference with the first embodiment will only be described.In this second embodiment, the pressurised zone towards inner chamber 25 of positioning piston 29 is greater than the pressurised zone of the free end 31 of actuator piston bar 7.Meanwhile, do not need as according to that spring required in the embodiment of Fig. 1 to 3, described spring by positioning piston 29 and actuator piston pushing separately.But, divide the position of the second end of the internal channel 26 being provided with oral area in the encapsulating surface of 8 most important at the thicker part of actuator piston bar 7.The second end of internal channel 26 should be arranged to be communicated with fluid-filled spaces 22 fluid when actuator piston dish 4 is in un-activated position, and should disconnect the connection of described fluid after actuator piston 4 leaves un-activated position at once.If do not disconnect internal channel 26 when actuator piston dish 4 is in active position, then incite somebody to action upwardly actuator piston, thus stop engine valve 15 correctly to close.
Possible modification of the present invention
The present invention not only limits to embodiment above-mentioned and illustrated in the accompanying drawings, and described embodiment only has the object of explaination and illustration.Present patent application is intended to all improvement projects and the flexible program that are encompassed in preferred embodiment described herein, therefore the present invention is limited by the wording of claim of enclosing, thus can in the scope of claim of enclosing according to all feasible modes to revise equipment.
It should also be noted that all about/relate to the information of term, such as top, below, upper and lower etc. be all to be understood that/be read as according to each figure orientation equipment, wherein, each accompanying drawing is directed by this way to be made it possible to read reference character according to suitable mode.Therefore, these terms only show the correlation of the embodiment illustrated, if equipment according to the present invention is provided with other structure/design, then described relation can change.
It should be pointed out that even without explicitly point out a specific embodiment feature can with the Feature Combination of another embodiment, but when feasible, this also should be considered as is apparent.
Claims (4)
1., for moving axially the actuator of the scavenging air valve in internal-combustion engine, described actuator comprises:
-actuator piston dish (4);
-actuator piston bar (7), described actuator piston bar is fixedly connected to described actuator piston dish (4) and axially stretches out from described actuator piston dish, and described actuator piston bar forms actuator piston together with described actuator piston dish;
-cylinder body volume, described cylinder body container is divided into first portion (5) and second portion (6) by described actuator piston dish (4), and described actuator piston dish can axially move back and forth in described cylinder body volume between un-activated position and active position;
-pressure fluid circuit (10), described pressure fluid circuit be arranged to for the described first portion (5) of described cylinder body container controllably fluid be communicated with; With
-the first oil hydraulic circuit (21), described first oil hydraulic circuit comprises fluid-filled spaces (22), described actuator piston bar (7) is arranged to along with described actuator piston dish (4) moving axially and moving axially relative to described fluid-filled spaces (22) in described cylinder body container, it is characterized in that, described actuator piston comprises the second oil hydraulic circuit (24), described in when described actuator piston dish (4) is in described un-activated position, the described fluid-filled spaces (22) of the first oil hydraulic circuit (21) is communicated with inner chamber (25) fluid in described second oil hydraulic circuit (24), described inner chamber (25) is partly defined by positioning piston (29), described positioning piston can axially move back and forth relative to described actuator piston and described positioning piston is arranged to press against and is arranged on the described scavenging air valve of described second portion (6) of described cylinder body volume, described second oil hydraulic circuit (24) comprises valve (27), described valve is arranged to stop fluid to flow from described inner chamber (25), described actuator piston bar (7) has free end (30), described free end is arranged to when described actuator piston dish (4) is in described un-activated position at least partly against the stop surface (31) in described fluid-filled spaces (22), the pressurised zone towards described inner chamber (25) of described positioning piston (29) is equal to or less than the pressurised zone of the free end (30) of described actuator piston bar (7).
2. actuator according to claim 1, wherein, the described valve (27) of described second oil hydraulic circuit (24) is safety check.
3. actuator according to claim 1 and 2, wherein, by spring (32) by described positioning piston (29) along in the described second portion (6) being biased into described cylinder body volume direction ground bias voltage.
4. the actuator according to any one in claims 1 to 3, wherein, described actuator piston bar (7) has hydraulic brake system in the region of its free end (30), and described hydraulic brake system is arranged to the movement velocity reducing described actuator piston before the free end (30) of described actuator piston bar (7) contacts described stop surface (31).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| SE1250793-5 | 2012-07-06 | ||
| SE1250793A SE543886C2 (en) | 2012-07-06 | 2012-07-06 | Actuator for axial displacement of a gas exchange valve at an internal combustion engine |
| PCT/SE2013/050780 WO2014007727A1 (en) | 2012-07-06 | 2013-06-26 | Actuator for axial displacement of a gas exchange valve in a combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104641080A true CN104641080A (en) | 2015-05-20 |
| CN104641080B CN104641080B (en) | 2017-06-23 |
Family
ID=49882341
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380035998.2A Active CN104641080B (en) | 2012-07-06 | 2013-06-26 | Actuator for moving axially the scavenging air valve in internal combustion engine |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US9228459B2 (en) |
| EP (1) | EP2872748B1 (en) |
| JP (1) | JP6200499B2 (en) |
| KR (1) | KR20150036415A (en) |
| CN (1) | CN104641080B (en) |
| BR (1) | BR112015000007A2 (en) |
| RU (1) | RU2628465C2 (en) |
| SE (1) | SE543886C2 (en) |
| WO (1) | WO2014007727A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113217135A (en) * | 2021-05-12 | 2021-08-06 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic fully variable valve driving mechanism |
| CN115142927A (en) * | 2022-07-28 | 2022-10-04 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic fully variable valve driving mechanism |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BG66834B1 (en) * | 2014-07-04 | 2019-02-28 | „Ел Ти Ей Джи“ Оод | Actuator for axial displacement of a gas exchange valve in an internal combustion engine |
| SE539632C2 (en) * | 2014-10-15 | 2017-10-24 | Freevalve Ab | Gas exchange valve actuator and internal combustion engine include gas exchange valve actuator |
| SE540421C2 (en) * | 2015-04-16 | 2018-09-11 | Freevalve Ab | Actuator for axial displacement of an object |
| SE540569C2 (en) | 2017-03-16 | 2018-10-02 | Freevalve Ab | Internal combustion engine and method for controlling such an internal combustion engine |
| SE542266C2 (en) * | 2017-09-11 | 2020-03-31 | Freevalve Ab | Internal combustion engine and method for controlling such an internal combustion engine |
| SE541697C2 (en) | 2017-09-11 | 2019-11-26 | Freevalve Ab | Internal combustion engine and method for controlling such an engine in a lowload mode |
| EP3479667A1 (en) | 2017-11-02 | 2019-05-08 | Melos GmbH | Artificial turf maintenance robot |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1659363A (en) * | 2002-05-30 | 2005-08-24 | 卡尔克内工程公司 | A device and a method for the generation of pressure pulses |
| US7040266B1 (en) * | 2005-05-10 | 2006-05-09 | Gm Global Technology Operations, Inc. | Electro-hydraulic engine valve actuation |
| US20060185633A1 (en) * | 2005-02-23 | 2006-08-24 | Chung Ha T | Electromechanical valve actuator |
| CN101675216A (en) * | 2007-04-16 | 2010-03-17 | 史古德利集团有限责任公司 | Variable valve actuator with a pneumatic booster |
| US20110168111A1 (en) * | 2010-01-11 | 2011-07-14 | Gm Global Technology Operations, Inc. | Engine including hydraulically actuated valvetrain and method of valve overlap control |
Family Cites Families (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4796573A (en) * | 1987-10-02 | 1989-01-10 | Allied-Signal Inc. | Hydraulic engine valve lifter assembly |
| US5193495A (en) * | 1991-07-16 | 1993-03-16 | Southwest Research Institute | Internal combustion engine valve control device |
| US5529030A (en) * | 1992-02-26 | 1996-06-25 | Rose; Nigel E. | Fluid actuators |
| JP3321918B2 (en) * | 1993-07-07 | 2002-09-09 | 日産自動車株式会社 | Valve control device for internal combustion engine |
| DE19728479C2 (en) * | 1997-07-05 | 2001-08-30 | Daimler Chrysler Ag | Device for actuating a gas exchange valve with an electromagnetic actuator |
| US6412457B1 (en) | 1997-08-28 | 2002-07-02 | Diesel Engine Retarders, Inc. | Engine valve actuator with valve seating control |
| FR2829178B1 (en) * | 2001-09-06 | 2006-03-03 | Peugeot Citroen Automobiles Sa | DEVICE FOR CONTROLLING AN INTERNAL COMBUSTION ENGINE VALVE |
| SE522163C2 (en) * | 2002-05-30 | 2004-01-20 | Cargine Engineering Ab | Method and device for pressure pulse generation |
| DE10239750A1 (en) * | 2002-08-29 | 2004-03-11 | Ina-Schaeffler Kg | Intake device for hydraulic pref. variable valve drive of IC engines has intake piston projecting with one end rod-like from housing, and play compensation element fastened to rod part via pressure piston |
| RU2338075C2 (en) * | 2004-10-18 | 2008-11-10 | Георгий Владимирович Голубенко | Ice cam gear drive and valve travel speed control method |
| JP2008527239A (en) * | 2005-02-02 | 2008-07-24 | エムエーエヌ・ディーゼル・エーエス | Large 2-cycle diesel engine with hydraulically operated exhaust gas valve |
| US7290509B2 (en) * | 2005-08-01 | 2007-11-06 | Zheng Lou | Variable valve actuator |
| SE531265C2 (en) * | 2006-01-16 | 2009-02-03 | Cargine Engineering Ab | Method and apparatus for driving a valve to the combustion chamber of an internal combustion engine, and an internal combustion engine |
| SE544218C2 (en) * | 2011-10-21 | 2022-03-08 | Freevalve Ab | Pressure fluid controlled actuator |
-
2012
- 2012-07-06 SE SE1250793A patent/SE543886C2/en unknown
-
2013
- 2013-06-26 BR BR112015000007A patent/BR112015000007A2/en not_active Application Discontinuation
- 2013-06-26 EP EP13813244.4A patent/EP2872748B1/en active Active
- 2013-06-26 WO PCT/SE2013/050780 patent/WO2014007727A1/en active Application Filing
- 2013-06-26 CN CN201380035998.2A patent/CN104641080B/en active Active
- 2013-06-26 KR KR20157003169A patent/KR20150036415A/en not_active Application Discontinuation
- 2013-06-26 RU RU2015103924A patent/RU2628465C2/en active
- 2013-06-26 JP JP2015520121A patent/JP6200499B2/en not_active Expired - Fee Related
- 2013-06-26 US US14/408,625 patent/US9228459B2/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1659363A (en) * | 2002-05-30 | 2005-08-24 | 卡尔克内工程公司 | A device and a method for the generation of pressure pulses |
| US20060185633A1 (en) * | 2005-02-23 | 2006-08-24 | Chung Ha T | Electromechanical valve actuator |
| US7040266B1 (en) * | 2005-05-10 | 2006-05-09 | Gm Global Technology Operations, Inc. | Electro-hydraulic engine valve actuation |
| CN101675216A (en) * | 2007-04-16 | 2010-03-17 | 史古德利集团有限责任公司 | Variable valve actuator with a pneumatic booster |
| US20110168111A1 (en) * | 2010-01-11 | 2011-07-14 | Gm Global Technology Operations, Inc. | Engine including hydraulically actuated valvetrain and method of valve overlap control |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113217135A (en) * | 2021-05-12 | 2021-08-06 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic fully variable valve driving mechanism |
| CN113217135B (en) * | 2021-05-12 | 2022-02-08 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic fully variable valve driving mechanism |
| CN115142927A (en) * | 2022-07-28 | 2022-10-04 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic fully variable valve driving mechanism |
| CN115142927B (en) * | 2022-07-28 | 2023-09-08 | 无锡威孚高科技集团股份有限公司 | Electric control hydraulic full-variable valve driving mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| SE1250793A1 (en) | 2014-01-07 |
| EP2872748A4 (en) | 2016-04-20 |
| JP2015522120A (en) | 2015-08-03 |
| BR112015000007A2 (en) | 2017-08-01 |
| EP2872748B1 (en) | 2018-11-14 |
| KR20150036415A (en) | 2015-04-07 |
| WO2014007727A1 (en) | 2014-01-09 |
| EP2872748A1 (en) | 2015-05-20 |
| RU2628465C2 (en) | 2017-08-17 |
| CN104641080B (en) | 2017-06-23 |
| US20150184558A1 (en) | 2015-07-02 |
| SE543886C2 (en) | 2021-09-14 |
| US9228459B2 (en) | 2016-01-05 |
| JP6200499B2 (en) | 2017-09-20 |
| RU2015103924A (en) | 2016-08-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104641080A (en) | Actuator for axial displacement of a gas exchange valve in a combustion engine | |
| JP4994455B2 (en) | Fluid working machine and valve configuration | |
| US9885261B2 (en) | Actuator for axial displacement of an object | |
| CN104081011A (en) | Actuator | |
| CN107567535B (en) | Actuator for axial movement of an object | |
| CN102414402A (en) | A control arrangement for an inlet valve in a piston engine | |
| CN101910605A (en) | Over time motor and control valve assembly in operating have been reduced | |
| RU2651002C2 (en) | Actuator for axial displacement of object | |
| JP6296948B2 (en) | Fuel injection valve | |
| CN101067388B (en) | Valve actuator assembly having a center biased spool valve with positioning member | |
| CN102852685A (en) | A fuel valve for large turbocharged two stroke diesel engines | |
| CN107690509B (en) | Pneumatic actuator for engine valve | |
| CN104454066A (en) | Continuous and variable lift driver | |
| US10808661B2 (en) | Fuel injection device | |
| JP6172113B2 (en) | Fuel injection valve | |
| CN107288699B (en) | Piezoelectrically driven camshaft-free valve driving mechanism | |
| JP5592741B2 (en) | Fuel injection valve | |
| JP2016050562A (en) | Fuel injection valve | |
| WO2018037714A1 (en) | Fuel injection device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |